JPH1047335A - Reciprocating piston engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact and sound structure while preventing an overload in an edge region of a thin thickness bearing shell, by using a simple and inexpensive means. SOLUTION: A structure is constituted by having a crankshaft 1 and a bearing device additionally provided in the crankshaft 1, and in the bearing device, an inner side bearing shell 9 of relatively thin thickness and an outer side support ring 7 additionally provided in the bearing shell 9 are provided. Particularly in a reciprocating piston engine for a large size Diesel engine, the support ring 7, in an angle region with at least bearing force leading to a maximum, in at least one side, has an elastic region provided corresponding to an edge part in an end face side of the bearing shell 9, this elastic region is arranged in a radial direction inner side of at least one elasticity giving recessed parts 10, 11 of the support ring 7.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention comprises a crankshaft and a bearing device attached to the crankshaft. The bearing device includes a relatively thin inner bearing shell and a bearing shell. A reciprocating piston engine, especially for heavy duty diesel engines, provided with an adapted outer support ring.

[0002]

2. Description of the Related Art When driven, a large force acts on the crankshaft, which causes bending and twisting of the crankshaft in addition to a large reaction force in the area of the bearing. It has been found empirically that this results in a high load on the edge region of the bearing shell. To cope with this, a device is provided for accommodating the bearing shell on a rocking bearing device for the main bearing of the crankshaft of a large diesel engine. This oscillating bearing device has a rotational degree of freedom about an oscillating shaft extending in a direction transverse to the bearing shaft. However, it has been found that this type of device is extremely complex and expensive to manufacture, since in addition to the original bearing surface the bearing surface of the oscillating bearing device must also be formed. Apart from this, the known device requires high maintenance costs, since it is very sensitive to relative movements in the area of the rocking bearing device and is prone to failure.

In another known solution, the bearing shell projects beyond the support ring. However, this type of device has also proven to be very sensitive (prone to failure) and requires a relatively large installation space, which is undesirable. Thus, the known devices have proven to be neither simple nor sufficiently reliable.

[0004]

SUMMARY OF THE INVENTION Accordingly, the present invention provides an improved device of the kind mentioned at the outset to overcome the above-mentioned disadvantages by means of simple and inexpensive means, whereby the edge of the thin-walled bearing shell is improved. It is an object of the invention to prevent overloading of the area and to achieve a simple and inexpensive manufacture and a compact and robust structure with it.

[0005]

SUMMARY OF THE INVENTION According to the invention, it is an object of the invention to provide a support ring, at least on one side, at least in the angular range in which the bearing force reaches a maximum, corresponding to the end face side edge of the bearing shell. Having an elastic region provided as
This is solved by arranging the elastic region radially inside at least one elasticity-imparting recess of the support ring.

Since the support ring is easily elastically deformed in a region where a large axial force is generated by one or a plurality of elastic regions formed by one or a plurality of elastic imparting recesses, the support ring is installed on the support ring and the support ring. The bearing shell is capable of following the deformation of the crankshaft.
As a result, the load on the bearing shell is also substantially uniform throughout. Also, local overload of the edge region is prevented. This results in a device according to the invention, since only elastic movement occurs and does not require a relatively movable bearing surface.
No maintenance is required and failures are reduced. The degree of freedom provided by the elastic flexibility allows the bearing shell to be supported axially in its entirety, so that the available space is fully utilized and the supporting bearing surface is maximized. . This also allows the bearing housing to have a relatively slim and lightweight structure. Another advantage of the measure according to the invention is that the elasticity recesses, which impart the desired elasticity to one or more elastic regions, can be formed more simply and cheaper than the bearing surface. The measures according to the invention thus guarantee excellent economics.

[0007] Preferred embodiments and advantageous embodiments of the above measures are set out in the dependent claims. Advantageously, the one or more elasticity recesses are eccentric with respect to the bearing shaft and / or have an asymmetric recess shape with respect to the machine central longitudinal plane and / or with respect to the transverse plane. This makes it possible in a suitable way to better adapt the elastic properties obtained by the one or more elasticity-imparting recesses to the actual load distribution which is normally not symmetrical in the longitudinal and transverse directions.

In many cases, it has been found to be advantageous to provide a number of identical or different elasticity recesses. This makes it possible to optimally adapt the elasticity of the elastic region to a specific load distribution.

In a preferred embodiment, at least one elasticity providing recess is formed as an elasticity providing groove. This provides good elasticity over a large surrounding area.

In another embodiment of the above means,
At least one elasticity providing recess is formed as a through hole or a bag-like hole. Thereby, higher rigidity can be obtained as compared with the case where the groove is provided. Also, the holes and the like can be formed very easily.

In another embodiment of the above means,
At least one elasticity recess is provided through the support ring. This enables a good reaction of the bearing to large pressures in a favorable manner, which is also favorable for a uniform load on the bearing shell. In this connection, it is desirable for the two elasticity-imparting recesses located opposite one another to be connected by at least one through recess, whereby particularly good results are obtained.

[0012] Further preferred structures and advantageous embodiments of the above measures are set out in the remaining dependent claims and will be apparent from the following description of embodiments.

[0013]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, description will be made with reference to the drawings. FIG. 1 is a side view schematically showing a first embodiment of a main bearing of a crankshaft of a large diesel engine according to the present invention. FIG. 2 is a sectional view taken along the line II-II in FIG. FIG. 3 is a side view showing another embodiment of the main bearing of the crankshaft according to the present invention, similarly to FIG. FIG. 4 is a sectional view taken along the line IV-IV in FIG. The basic structure of the two embodiments is identical. Accordingly, the following description is based on the
One embodiment relates to one embodiment.

The construction and operation of large two-stroke diesel engines are known per se and will not be described in further detail herein. In order to convert the reciprocating piston movement into rotary movement, a crankshaft 1 is provided in the lower engine area, which extends over the entire engine length. The crankshaft has journals 2 which are aligned with each other and are journaled by the journal on the base side.

For this purpose, a so-called main bearing is provided, which is divided by a horizontal separating seam 3 into a lower part 4 and an upper part 5. The lower part 4 is fixed and integrated in the base structure. The upper part 5 is formed as a removable lid, and is correspondingly indicated simply in broken lines in FIGS. 1 and 3. 2 and 4, the upper part 5 is completely omitted.

The base is formed in the area of the main bearing as shown in FIGS. 1 and 3 so as to have a gate shape with two lateral case parts 6 and is illustrated through these case parts. Not tie rod is inserted. The side case 6 supports the lower part 4 of the main bearing. This lower part consists of a solid support ring 7, which is connected in a T-shape as a half-ring collar to a wall 8 connecting the two case parts 6 to one another. Therefore, the wall portion 8 functions as a fin-shaped reinforcing member for the support ring 7. A thin bearing shell 9 is inserted into the bearing hole for the lower part 4 and the upper part 5, and this bearing shell is composed of a thin bearing half shell corresponding to the lower part 4 and the upper part 5, respectively. . FIG.
As shown in FIG. 4 and FIG. 4, the lower side of the bearing shell 9 is supported over the entire axial direction by corresponding components of the support ring 7. The thin half-shell of the bearing shell 9 inserted into the bearing hole of the upper part 5 can be similarly supported.

The crankshaft 1 is deformed by receiving a load.
The deformation and the resulting bearing load fluctuate according to the crank angle. In order to prevent overloading of the bearing shell 9 made of a thin and very thin and very strong material, the variable displacement of the rotating crankshaft 1 at least where the maximum bearing force occurs in the bearing shell. Is provided, and the bearing load is made uniform. For this purpose, the area connected to the bearing shell 9 of the main bearing and supporting the bearing shell is formed elastically so that it can carry out an elastic movement following the deformation of the rotating crankshaft 1. . Thereby, the bearing shell 9 can be deformed in accordance with the deformation of the rotating crankshaft 1, and the occurrence of a peak value in the load on the bearing shell 9 is prevented. It is preferable that the change in the elasticity enhanced by the elasticity applying means follows the change in the bearing force as the bearing force increases within the angle range including the maximum value of the bearing force.

The removable upper part 5 is a relatively elastic component. Therefore, in the region of the upper portion 5, even if a large force is generated in this region, usually, other elasticity imparting means is not required or only a small amount is required. In a device of the type shown in the figure,
The maximum load occurs in the angular range in the lower part 4. The lower part 4 integrated into the base structure is a relatively hard area. However, by using an appropriate elasticity imparting means, the support ring 7 which is connected to the bearing shell 9 and supports the bearing shell can be used.
The desired elasticity is imparted to the region.

At least the region of the support ring 7 that supports the edge region in the axial direction of the bearing shell 9 is formed as an elastic region having a large elasticity. In order to achieve this, the support ring 7 is provided with an elasticity-imparting recess located radially outward with respect to the joint surface with the bearing shell 9 and located in the end face region. This recess is the groove 10,
It can be formed as a bag-like hole 11, a through slit 12, a through hole 13, or the like. These shapes are provided in various combinations. The respective arrangement and shape of the elasticity imparting recesses, that is, the configuration of the recesses, are determined based on the expected deformation in the crankshaft 1 that fluctuates with the rotation of the crankshaft 1 and the bearing load distribution caused thereby. In an angle region where a load is high and a large amount of elasticity is required, a large amount of elasticity is provided by appropriately forming the elasticity providing recess, and a small amount of elasticity is provided in a region where the load is small. Can be

In the embodiment shown in FIGS. 1 and 2, one elasticity providing groove 10 and two elasticity providing bag-like holes 11 are formed in the region of the end face of the support ring 7 shown in FIG. ing. In this embodiment, the elasticity imparting recesses are such that the recess shape does not have a central axis and a plane of symmetry, and is therefore eccentric with respect to the axis and asymmetrical with respect to the machine central vertical plane and other vertical planes. Are formed. In this case, the elasticity imparting groove 10 is provided in the left quadrant of FIG. The elasticity-imparting bag-shaped hole 11 is provided in the right quadrant of FIG. The elasticity providing groove portion 10 extending in a curved manner along the length direction is eccentrically arranged with respect to the bearing shaft. By using the asymmetrical and eccentric concave shape as described above, the driving characteristics when the crankshaft of a combustion machine having a reciprocating piston, such as a large diesel engine, rotates can be best secured.

The depth and the cross-sectional shape of the elasticity imparting groove 10 can be made variable along the length of the groove.
At this time, it is preferable to change gradually. In the embodiment shown in FIG. 1, the resilient groove 10 is flat and narrow and closed in the lower top region of the bearing, which corresponds to a linear change along the length.
Similarly, the diameter of the elasticity imparting bag-shaped hole 11, the distance from the bearing shell 9, and the depth of the elasticity imparting bag-shaped hole 11 can be made different. In the embodiment shown, the elasticity-imparting bladder hole 11 closest to the lower apex region has the largest diameter, which diameter is larger than the inner width of the elasticity-imparting groove 10.

In the end face region on the opposite side of the support ring 7, as is apparent from FIG. The shape and arrangement of this recess is independent of the elasticity imparting recess provided on the opposite end face,
It is determined based on the predicted deformation of the crankshaft in that region. In the illustrated embodiment, the elasticity imparting groove 1 is also provided in the region of the end surface of the support ring 7 shown on the right in FIG.
0 is provided. However, this groove has a smaller depth and a smaller inner width than the elasticity-imparting groove 10 on the opposite side. The radial distance from the bearing shell 9 is greater than on the opposite side. The same applies to the elasticity-imparting bag-shaped holes provided in some cases. The elasticity-imparting bag-shaped hole does not need to be associated with the opposite hole. By the way, in the illustrated embodiment, the elasticity imparting bag-shaped hole 11 is provided. However, it is also conceivable to form a through hole. Similarly, elasticity-imparting slits are provided between elasticity-imparting grooves 10 located in opposite directions, so that the penetration from one side to the other extends over the entire length or part of the length of the groove 10. It is also conceivable to form

In the embodiment shown in FIGS. 3 and 4,
Unlike the embodiment shown in FIGS. 1 and 2, in the region of both end faces of the support ring 7,
Each of the elasticity providing grooves 10 symmetrical with respect to the machine center vertical plane is formed. The resilient groove extends in this embodiment over a large angular range of approximately 160 °, with its end reaching the vicinity of the separating seam 3. Furthermore, in addition to the elasticity-imparting grooves 10, a through-elasticity-imparting slit 12, which is symmetrical with respect to the machine center longitudinal plane and extends over an angle range of about 30 °, connects the elasticity-imparting grooves 10 in the two end face regions to each other, Further, an elasticity providing hole portion 13 formed on the side of the elasticity imparting slit and also penetrating therethrough is provided, and the diameter of the elasticity imparting hole portion is smaller than the inner width of the elasticity imparting slit 12 penetrated.

As described above, since the elasticity imparting concave portion is located substantially outside the joint surface with the bearing shell 9, FIG.
As is clear from FIG. 4 and FIG. 4, a thin supporting region 14 for supporting the bearing shell 9 is formed. This support region is formed as a flange for the elasticity providing groove 10. In the illustrated embodiment, the inner width of the elasticity imparting groove 10 increases outward. Accordingly, the thickness of the flange decreases outward. The amount of elastic deformation of the support region 14 thus formed increases toward the end face side of the support ring 7.

In the region of the elasticity-imparting grooves 10 facing each other, a bridge 15 is formed which is located between them, which can be off-center as shown in FIG. 2 or as shown in FIG. Located in the center. The structure of the end face of the bridge 15 corresponds to the structure of the bottom of the groove. In the embodiment shown in FIG. 4, the inside of the two elasticity providing grooves in the end face region is formed round. Accordingly, the bridge 15 has an end surface that is concave inward. In the embodiment shown in FIG. 2, one elasticity providing groove 10 has a flat groove bottom, and the opposite elasticity providing groove 10 has a curved groove bottom. Accordingly, the bridge 15 has a flat end face and an inwardly concave end face. The end face side area of the support area 14 can be elastically displaced in the radial direction by a corresponding elasticity imparting recess,
Along with this, it functions as an elastic region for elastically supporting the bearing shell 9. The bridge 15 can be displaced in the direction of the end face, and accordingly functions as an elastic hinge. Thereby, a favorable elastic displacement can be given to the support portion of the bearing shell 9 as a whole. Therefore, the bearing shell can be supported by the support ring 7 over the entire axial direction.

In this embodiment, the amount of displacement of the end surface side region of the support region 14 supporting the bearing shell 9 and the amount of displacement of the bridge are provided by the penetrating elastic concave portion having the shape of the elastic slit 12 and the elastic hole portion 13. The resilience of the bearing shell 9 can be adapted to the load, since the resilience of the bearing shell 15 is further increased and a suitable resilience is produced in the radial direction. Therefore, there is no need to worry about local overload of the bearing shell 9. Rather, a substantially uniform load distribution over the entire length and width direction, i.e., over the entire bearing surface, of the lower part of the bearing shell 9 corresponding to the bearing shell 9 or the lower part 4 is obtained by the above-described measures. Accordingly, since the entire bearing surface is optimally used, a bearing structure having a relatively small axial length and correspondingly slim as a whole can be realized.

In the region of the upper part 5, such elasticity-imparting means as described above are not normally required. This is because, unlike the lower part 4, the upper part 5 is not solid.
However, it is also conceivable to form an elastic region as described above by providing an elasticity imparting concave portion also in the region of the upper portion 5.

In the illustrated example, the provided elasticity providing recess is empty. However, for example, the elasticity imparting groove 10
Or elasticity imparting bag-shaped hole 11 or elasticity imparting slit 1
It is also conceivable to fill the elasticity imparting concave portion having the shape of the elasticity imparting hole portion 2 or to insert an elastic reinforcing member integrally with the support ring 7.

[Brief description of the drawings]

FIG. 1 is a side view schematically showing a first embodiment of a main bearing of a crankshaft of a large diesel engine according to the present invention.

FIG. 2 is a sectional view taken along the line II-II in FIG.

FIG. 3 is a side view showing another embodiment of the main bearing of the crankshaft according to the present invention, similarly to FIG.

FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Crankshaft 7 Support ring 9 Bearing shell 10, 11, 12, 13 Elasticity giving recess 14 Elastic area 15 Bridge

Claims (16)

[Claims] The invention comprises a crankshaft (1) and a bearing device attached to the crankshaft. The bearing device includes a relatively thin inner bearing shell (9) and a bearing shell. In a reciprocating piston engine, in particular for large diesel engines, provided with an associated outer support ring (7), said support ring (7) has at least one side, at least in the angular region where the bearing force reaches a maximum. And an elastic region (14) provided corresponding to an edge on the end face side of the bearing shell (9), and the elastic region is formed by at least one elasticity concave portion (10) of the support ring (7). , 11,
12. A reciprocating piston engine which is arranged radially inward of (13). 2. The reciprocating piston engine according to claim 1, wherein the elastic region is provided in an end surface region on both sides of the support ring. 3. The reciprocating piston engine according to claim 1, wherein the elasticity-imparting recesses (10, 11) are provided in end regions on both sides of the support ring (7). . 4. The reciprocating device according to claim 1, wherein at least one elasticity recess (12, 13) penetrating the support ring (7) is provided. Piston engine. 5. The reciprocating piston engine according to claim 1, wherein a plurality of the same or different elasticity providing recesses (10, 11, 12, 13) are provided. . 6. One or more of the elasticity recesses (10, 11, 12, 13) are eccentric with respect to the bearing axis and / or asymmetric with respect to the machine center longitudinal plane and / or the transverse plane. The reciprocating piston engine according to any one of claims 1 to 5, wherein the reciprocating piston engine has a concave shape. 7. The at least one elasticity providing recess (1)
The reciprocating piston engine according to any one of claims 1 to 6, wherein 0) is formed as an elasticity providing groove. 8. The reciprocating piston engine according to claim 7, wherein a depth and / or a cross-sectional shape of the groove-shaped elasticity providing recess (10) changes linearly. 9. The at least one elasticity providing recess (1)
9. The reciprocating piston engine according to claim 1, wherein 1) is formed as an elasticity imparting hole. 10. The two elasticity recesses (10) located on opposite sides are connected by at least one elasticity recess (12, 13) passing through a bridge (15) provided between the elasticity recesses. The reciprocating piston engine according to any one of claims 1 to 9, wherein 11. The reciprocating piston engine according to claim 10, wherein at least one of the penetrating elasticity providing recesses (12) is formed as a through slit. 12. The bridge (15), preferably being a number of elasticity-imparting holes arranged beside the through slit.
The reciprocating piston engine according to claim 10 or 11, wherein at least one elasticity providing hole (13) penetrating through is provided. 13. The elasticity providing recesses (10, 11, 1)
13. The reciprocating piston engine according to claim 1, wherein at least part of the reciprocating piston engine is filled with an elastic material. 14. The split bearing according to claim 1, wherein at least one elastic region is provided at least in the region of the lower bearing part. A reciprocating piston engine according to any of the above. 15. One or more elasticity providing recesses (1)
0, 11, 12, and 13) (1)
The elasticity imparting recess is formed and / or arranged so that the elasticity of 4) has a change adapted to a change in bearing force in a predetermined angular range of the elastic region. The reciprocating piston engine according to any one of claims 1 to 14. 16. The support ring (7) of the bearing device attached to the crankshaft (1) has at least one
Means are provided for reducing the stiffness of the two elasticity recesses (10, 11, 12, 13), whereby the change in the reduction of the stiffness within a predetermined angular range causes the change in the rotating crankshaft (1). 17. The method according to claim 1, wherein the elasticity-imparting recesses are arranged and formed eccentrically and asymmetrically so as to have a change adapted to the change in the bearing load caused by the method. A reciprocating piston engine according to any of the above.